EP3880947B1 - Kolbenbrennkraftmaschine mit generator - Google Patents

Kolbenbrennkraftmaschine mit generator Download PDF

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Publication number
EP3880947B1
EP3880947B1 EP19888311.8A EP19888311A EP3880947B1 EP 3880947 B1 EP3880947 B1 EP 3880947B1 EP 19888311 A EP19888311 A EP 19888311A EP 3880947 B1 EP3880947 B1 EP 3880947B1
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EP
European Patent Office
Prior art keywords
crankshaft
internal combustion
generator
cylinders
engine
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EP19888311.8A
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English (en)
French (fr)
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EP3880947A1 (de
EP3880947A4 (de
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Vaclav Knob
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/10—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with more than one main shaft, e.g. coupled to common output shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B21/00—Combinations of two or more machines or engines
    • F01B21/02—Combinations of two or more machines or engines the machines or engines being all of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/06—Engines with means for equalising torque
    • F02B75/065—Engines with means for equalising torque with double connecting rods or crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
    • F02B75/225—Multi-cylinder engines with cylinders in V, fan, or star arrangement having two or more crankshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/24—Compensation of inertia forces of crankshaft systems by particular disposition of cranks, pistons, or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/22—Compensation of inertia forces
    • F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
    • F16F15/264—Rotating balancer shafts
    • F16F15/265—Arrangement of two or more balancer shafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L2270/00—Problem solutions or means not otherwise provided for
    • B60L2270/10—Emission reduction
    • B60L2270/14—Emission reduction of noise
    • B60L2270/145—Structure borne vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
    • F02B75/18—Multi-cylinder engines
    • F02B2075/1804—Number of cylinders
    • F02B2075/1808—Number of cylinders two
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/04—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for electric generators
    • F02B63/042—Rotating electric generators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups

Definitions

  • the present invention relates to a piston internal combustion engine in coupling with a generator comprising a two-cylinder engine or engine with multiplication of two cylinders with two crankshafts for recharging accumulators in vehicles or airplanes with minimized vibration during operation, so-called range extender.
  • Piston internal combustion engines of various types are used to drive a generator.
  • Single and multi-cylinder units are used. Virtually every engine can be coupled to a generator, and so internal combustion engines based on engines for driving other devices are generally used. They usually have one crankshaft and drive one generator.
  • These designs although multi-cylinder and well balanced in terms of inertia forces, have torsional vibration, which is caused by individual firing events in the engine cylinders and the immediate reaction of the engine block.
  • range extender type for example for electric vehicles or electric planes, are specific. Requirements are, for example, simplicity, low number of cylinders, low weight, suitable installation dimensions and minimization of vibration.
  • the engine is designed to drive alternator and aero plane propeller, which is rather different case but also seeks to reduce vibration.
  • the difference is that the crankshafts rotate to the same side and not to the opposite.
  • the reaction moments of individual engines during ignition in cylinders do not cancel with each other but add up.
  • the alternator and propeller are driven by the crankshafts through the gears, that change direction and speed of revolutions. These gears are heavily loaded and are a potential source of resonances and failures.
  • the principle is that, the first crankshaft with the gear is mounted parallel to the second crankshaft with the second gear in one engine case, such that the 1: -1 gears are engaged and the first crankshaft is coupled to the first generator rotor and the second crankshaft is coupled to the second generator rotor or flywheel, wherein the moment of inertia of the first crankshaft assembly with the first gear and the first generator rotor corresponds to the moment of inertia of the second crankshaft assembly with the second gear and second generator rotor or flywheel.
  • the cylinders with the pistons are positioned perpendicularly to the plane of symmetry between the crankshafts, with the axes of the pair of cylinders lying in the plane and both pistons being at the top dead center simultaneously.
  • the balancing of the individual crank mechanisms is done in such a way that the unbalanced rotating masses of the crank mechanism are 100% balanced by balance weights and so the centrifugal forces Fo cancel each other out.
  • the reciprocating masses of the crank mechanisms remain completely unbalanced.
  • the inertia forces Fs from the reciprocating masses cancel each other by the symmetrically opposite movement of the same reciprocating masses of both crank mechanisms in one plane.
  • the engine can be designed with two-stroke or four-stroke cycle. At four-stroke engine, the working cycle of the opposite cylinders can be shifted by one revolution.
  • the engine may comprise a plurality of opposed cylinder pairs with symmetrical placement of the pistons and connecting rods relative to the plane of symmetry between the two crankshafts, with the working cycles of the pairs of opposed cylinders being phase shifted.
  • the piston internal combustion engine with a generator ideally meets the requirements of the modern range extender for electrically powered vehicles and airplanes. It is a simple, inexpensive solution with only two cylinders, which is perfectly balanced in terms of inertia forces and moments.
  • the rotating masses on the crank mechanisms are 100% balanced and the inertia forces from the reciprocating masses are canceling each other due to the symmetrically opposite movement of the same reciprocating masses of the two crank mechanisms.
  • the flat design is advantageous for the most common types of internal combustion engine installations.
  • the forces transmitted to the crank mechanisms and their accelerations are for both equal, so the gears connecting the crankshafts will be loaded minimally.
  • the most advantageous arrangement is to use two identical generators on both crankshafts and then the gears will have only a synchronizing effect.
  • This arrangement is also advantageous because the two generators are smaller in diameter and do not increase the installation height of the engine.
  • the possibility of disconnecting one generator electrically in case of its failure may also be solved. If only one generator is used and only the flywheel is on the other shaft, then the gears will also transmit the useful power from the flywheel shaft. Even so, the load applied on the gearing will be very favorable.
  • the advantage is also that the engine can be developed into production relatively quickly and easily using the components of contemporary single-cylinder engines.
  • Fig. 1 is a cross-sectional view of a piston internal combustion engine with two cylinders with cylinder heads and pistons with connecting rods and two crankshafts connected by gears with a ratio of 1: -1, which means with the opposite direction of rotation.
  • the first crankshaft with the gear is mounted parallel to the second crankshaft with the second gear in one engine case such that the 1: -1 gears are engaged.
  • the first crankshaft is coupled to the first generator rotor and the second crankshaft is coupled to the second generator rotor.
  • the cylinders with the pistons are positioned perpendicularly to the plane of symmetry between the crankshafts, and the axes of the pair of cylinders are lying in the plane. Both pistons are at the top dead center simultaneously.
  • the engine has a two-stroke cycle.
  • the model piston internal combustion engine of Fig. 1 consists of the two cylinders 9 and 10 with the cylinder heads 13 and 14 and the pistons 11 and 12 with the connecting rods 7 and 8 and two crankshafts 1 and 2 , which are connected by the gears 3 and 4 with 1: -1 ratio, which means with the opposite direction of rotation.
  • the first crankshaft 1 with the gear 3 is mounted parallel to the second crankshaft 2 with the second gear 4 in one engine case 17 such that the gears are engaged.
  • the first crankshaft 1 is coupled to the first generator rotor 5 and the second crankshaft 2 is coupled to the second generator rotor 6 .
  • the moment of inertia of the first crankshaft assembly 1 with the first gear 3 and the first generator rotor 5 corresponds to the moment of inertia of the second crankshaft assembly 2 with the second gear 4 and the second generator rotor 6 .
  • the cylinders 9 and 10 with the pistons 11 and 12 are positioned perpendicular to the plane of symmetry 20 between the crankshafts, with the axes of the pair of cylinders lying in the plane and both pistons 11 and 12 located in the top dead center simultaneously.
  • the engine has a two-stroke cycle.
  • the model piston internal combustion engine with the generator of Fig. 2 is based on the embodiment of Fig. 1 . However, the engine has a four-stroke cycle.
  • the pistons 11 and 12 are located at the top dead center simultaneously and the ignitions occur in both cylinders at the time.
  • the model piston internal combustion engine with the generator of Fig. 3 is based on the embodiment of Fig. 1 .
  • a larger first generator rotor 5 is mounted on the first crankshaft 1 and a flywheel 18 is mounted on the second crankshaft 2 . To avoid colliding, they are axially offset.
  • the model piston internal combustion engine with the generator of Fig. 4 is based on the embodiment of Fig. 1 .
  • the first generator rotor 5 is mounted on the front of the first crankshaft 1 and the second generator rotor 6 is mounted on the rear of the second crankshaft 2 .
  • the generator rotors 5 and 6 have large outer diameters, but they do not interfere with each other in this arrangement.
  • the model piston internal combustion engine of the generator of Fig. 5 is based on the embodiment of Fig. 1 .
  • the engine differs in having two pairs of opposed cylinders 9 and 10.
  • the front pair of opposed cylinders has a working cycle shifted 180 ° from the rear pair of opposed cylinders.
  • the operation is following.
  • the first crankshaft 1 with the first gear 3 and the first generator rotor 5 rotates to the opposite side than the second crankshaft 2 with the second gear 4 and the second generator rotor 6 with the same speed due to the gears 3 and 4 with the gear ratio 1 : 1.
  • the first piston 11 and the second piston 12 move symmetrically with respect to the plane of symmetry 20 of the engine, so that they are always at the top dead center simultaneously.
  • the acceleration of the reciprocating masses of the first piston 11 is identical, but in the opposite direction to the acceleration of the reciprocating masses of the second piston 12, and at the same masses, the inertia forces Fs are completely eliminating each other.
  • the additional inertia moment of the first connecting rod Z and the second connecting rod 8 must also be considered. If the connecting rods are identical, these moments will also be identical but opposite and thus eliminated completely. Since the axes of the first cylinder 9 and the second cylinder 10 are in the same plane, no moment is generated from the inertia forces. The balancing of the rotating masses on the first crankshaft 1 as well as on the second crankshaft 2 is done in such a way that the unbalanced rotational masses are 100% balanced by balance weights 15 and 16 and the centrifugal forces F0 thus also cancel each other. The ignition in the first cylinder 9 and the ignition in the second cylinder 10 transmit torque to the generator rotors 5 and 6.
  • crankshafts 1 and 2 are synchronized by the gears 3 and 1, their angular accelerations are exactly the same but opposite. Since the moment of inertia of the first crankshaft assembly 1 with the first gear 3 and the first generator rotor 5 is equal to the moment of inertia of the second crankshaft assembly 2 with the second gear 4 and the second generator rotor 6, the reaction moments has the same magnitude but opposite sense and so the resulting reaction to the engine block is completely eliminated. Thus, the piston internal combustion engine does not transmit any forces or moments except its weight to its mounts during operation. In a two-stroke engine, simultaneous ignition occurs in the first cylinder 9 and the second cylinder 10.
  • the load between the first gear 3 and the second gear 4 is minimal.
  • the function of the gears 3 and 4 will only be to synchronize. Only slight differences will be compensated due to the different course of combustion in the first cylinder 9 and the second cylinder 10.
  • a common ignition in the first cylinder 9 and the second cylinder 10 or alternating ignition is possible when the working cycles are shifted 360°.
  • alternating ignition the operation of the generators 5 and 6 is smoother, but the gear loading of the gears 3 and 4 is significant, because the active crankshaft 1 must accelerate the second idle crankshaft 2 and vice versa.
  • the gears 3 and 4 will transmit power from the second crankshaft 2 to the crankshaft 1.
  • the loading of the gears 3 and 4 is relatively favorable. The advantage may be the use of only one generator.
  • the engine has several pairs of opposed cylinders 9 and 10 , its operation is similar to that of a two-cylinder version. Working cycles of the different pairs of cylinders 9 and 10 can be phase shifted, and then the operation of the generator rotors 5 and 6 will be smoother and the power output will be higher.
  • the piston internal combustion engine of the present invention finds application as a range extender generator type for modern electric vehicles and aircrafts.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Control Of Eletrric Generators (AREA)

Claims (6)

  1. Kolbenverbrennungsmotor mit einem Generator, bestehend aus mindestens zwei Zylindern (9) und (10) mit Köpfen (13) und (14) und Kolben (11) und (12) mit Pleuelstangen (7) und (8) und zwei Kurbelwellen (1) und (2), die durch Zahnräder (3) und (4) mit einem Übersetzungsverhältnis von 1 : -1 verbunden sind, d.h. mit entgegengesetzter Drehrichtung, dadurch gekennzeichnet, dass eine erste Kurbelwellenbaugruppe, die eine erste Kurbelwelle (1) mit einem ersten Zahnrad (3) umfasst, parallel zu einer zweiten Kurbelwellenbaugruppe, die eine zweite Kurbelwelle (2) mit einem zweiten Zahnrad (4) umfasst, in einem einzigen Motorgehäuse (17) angeordnet ist, so dass die Zahnräder mit dem Übersetzungsverhältnis 1: -1 ineinander passen, und die erste Kurbelwelle (1) ist mit dem ersten Generatorrotor (5) und die zweite Kurbelwelle (2) mit dem zweiten Generatorrotor (6) und/oder dem Schwungrad (18) verbunden, wobei das Trägheitsmoment der ersten Kurbelwellenbaugruppe (1) zusammen mit dem ersten Zahnrad (3) und dem ersten Generatorrotor (5) dem Trägheitsmoment der zweiten Kurbelwellenbaugruppe (2) zusammen mit dem zweiten Zahnrad (4) und dem zweiten Generatorrotor (6) und/oder dem Schwungrad (18) entspricht, und ferner sind die Zylinder (9) und (10) mit den Kolben (11) und (12) senkrecht zur Symmetrieebene (20) zwischen den Kurbelwellen so angeordnet, dass die Achsen des Zylinderpaares in der Ebene liegen und beide Kolben (11) und (12) sich im oberen Totpunkt gleichzeitig befinden.
  2. Kolbenverbrennungsmotor mit einem Generator nach Anspruch 1, dadurch gekennzeichnet, dass das Auswuchten der Kurbeltriebe so erfolgt, dass die unausgeglichenen Rotationsmassen der Kurbeltriebe durch Auswuchtgewichte (15) und (16) zu 100% ausgewuchtet werden und sich die Fliehkräfte Fo aufheben, wobei die Gleitmassen der Kurbeltriebe völlig unausgewuchtet bleiben und sich die Trägheitskräfte Fs der Gleitmassen aufgrund der symmetrisch entgegengesetzten Bewegung der identischen Gleitmassen der beiden Kurbeltriebe in derselben Ebene gegenseitig aufheben.
  3. Kolbenverbrennungsmotor mit einem Generator nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Motor ein Zweitaktmotor ist.
  4. Kolbenverbrennungsmotor mit einem Generator nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Motor ein Viertaktmotor ist.
  5. Kolbenverbrennungsmotor mit einem Generator nach Anspruch 3, dadurch gekennzeichnet, dass der Arbeitszyklus der gegenüberliegenden Zylinder um eine Umdrehung versetzt ist.
  6. Kolbenverbrennungsmotor mit einem Generator nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Motor mehrere gegenüberliegende Zylinderpaare (9), (10) mit symmetrischer Anordnung der Kolben (11), (12) und Pleuelstangen (7), (8) relativ zur Symmetrieebene (20) zwischen den beiden Kurbelwellen (1) und (2) aufweist, wobei die Arbeitszyklen der gegenüberliegenden Zylinderpaare phasenverschoben sein können.
EP19888311.8A 2018-11-27 2019-11-26 Kolbenbrennkraftmaschine mit generator Active EP3880947B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CZ2018-653A CZ308401B6 (cs) 2018-11-27 2018-11-27 Pístový spalovací motor s generátorem
PCT/IB2019/060163 WO2020109990A1 (en) 2018-11-27 2019-11-26 Piston internal combustion engine with generator

Publications (3)

Publication Number Publication Date
EP3880947A1 EP3880947A1 (de) 2021-09-22
EP3880947A4 EP3880947A4 (de) 2022-06-22
EP3880947B1 true EP3880947B1 (de) 2023-02-15

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US (1) US11085370B2 (de)
EP (1) EP3880947B1 (de)
KR (1) KR102398982B1 (de)
CN (1) CN113272539B (de)
CZ (1) CZ308401B6 (de)
ES (1) ES2944316T3 (de)
HU (1) HUE061937T2 (de)
RU (1) RU2769415C1 (de)
WO (1) WO2020109990A1 (de)

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DE102020125799A1 (de) * 2020-10-02 2022-04-07 Frank Obrist Luftfahrzeug
JP6932411B1 (ja) * 2021-05-07 2021-09-08 アラセ・アイザワ・アエロスパシアル合同会社 無人飛行体のエンジン装置

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DE102014115042A1 (de) * 2014-10-16 2016-04-21 Obrist Technologies Gmbh Stromaggregat
WO2016140323A1 (ja) * 2015-03-03 2016-09-09 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
JPWO2016139751A1 (ja) * 2015-03-03 2017-04-27 Ｚメカニズム技研株式会社 Ｘｙ分離クランク機構を備えた駆動装置
JP6794605B2 (ja) * 2016-04-18 2020-12-02 糸井ホールディングス株式会社 エンジン搭載型飛行装置
DE202018105331U1 (de) * 2018-02-26 2018-10-30 Obrist Technologies Gmbh Stromaggregat

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CN113272539B (zh) 2023-05-05
KR20210083363A (ko) 2021-07-06
US20200263602A1 (en) 2020-08-20
CZ2018653A3 (cs) 2020-06-03
US11085370B2 (en) 2021-08-10
WO2020109990A1 (en) 2020-06-04
KR102398982B1 (ko) 2022-05-17
RU2769415C1 (ru) 2022-03-31
CN113272539A (zh) 2021-08-17
EP3880947A1 (de) 2021-09-22
EP3880947A4 (de) 2022-06-22
CZ308401B6 (cs) 2020-07-29
HUE061937T2 (hu) 2023-09-28

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